Tensioner with spring force control in a second bore

ABSTRACT

A tensioner for tensioning a chain span which uses two pistons. The movement of the two pistons may be coupled together. The first piston provides damping to the chain span and a second piston provides variable, dominant and automatically adjusting spring force to the chain span. The tensioner automatically adjusts the mean tension force to keep the chain tension as low as possible without sacrificing chain control, significantly improving drive efficiency at new chain conditions and conditions with dynamic loads.

REFERENCE TO RELATED APPLICATIONS

This application is a divisional application of co-pending application Ser. No. 14/651,292, filed June 11, 2015, entitled, “TENSIONER WITH SPRING FORCE CONTROL IN A SECOND BORE”, which claims priority from International Application No. PCT/US2013/072574, entitled “TENSIONER WITH SPRING FORCE CONTROL IN A SECOND BORE”, which was filed on December 2, 2013, which claims the benefit of Provisional Application No. 61/738,547, entitled “TIMING DRIVE SPRING FORCE CONTROL TENSIONER”, filed December 18, 2012 and Provisional Application No. 61/774,059, entitled, “TENSIONER WITH SPRING FORCE CONTROL IN SECOND BORE”, filed March 7, 2013. The aforementioned applications are hereby incorporated herein by reference.

BACKGROUND OF THE INVENTION

Field of the Invention

The invention pertains to the field of tensioners. More particularly, the invention pertains to a tensioner with spring force control in a second bore of the housing.

Description of Related Art

Generally, in timing chains for valve drives of internal combustion engines, camshaft chains in use for a camshaft-camshaft drive, and balancer chains have tensioners that are used on the slack side of a chain to take up slack in the chain and to apply tension to the chain.

During operation, a piston of the tensioner presses against the chain to maintain tension in the chain. When tension in the chain increases during operation due to resonance of a chain span, a high load from the chain acts on the piston of the tensioner, causing the piston to extend as the tensioner pumps up to keep the tension in the chain.

Chain drive tensioner spring force is often too high for most operating conditions because the spring force needs to be sufficient to handle worst case operating conditions of the tensioner system. The effectiveness of the tensioner and the overall system behavior and efficiency could be improved if the tensioner spring force could be varied with operating conditions, taking into account wear and stretching that occurs in the chain during the life of the chain.

SUMMARY OF THE INVENTION

A tensioner for tensioning a chain span which uses two pistons. The movement of the two pistons may be coupled together. The first piston provides damping to the chain span and a second piston provides variable and automatically adjusting spring force to the chain span. The tensioner automatically adjusts the mean tension force to keep the chain tension as low as possible without sacrificing chain control, significantly improving drive efficiency at new chain conditions and conditions with dynamic loads.

BRIEF DESCRIPTION OF THE DRAWING

FIG. 1 shows a schematic of a tensioner of a first embodiment of the present invention.

FIG. 2a shows a schematic of a tensioner of a second embodiment tensioning a chain under normal operating conditions.

FIG. 2b shows a schematic of a tensioner tensioning a chain in response to high dynamic load.

FIG. 3a shows a schematic of a tensioner of a third embodiment tensioning a chain under normal operating conditions.

FIG. 3b shows a schematic of a tensioner tensioning a chain in response to high dynamic load.

FIG. 4a shows a schematic of a tensioner of a fourth embodiment tensioning a chain under normal operating conditions.

FIG. 4b shows a schematic of a tensioner tensioning a chain in response to high dynamic load.

FIG. 5 shows a schematic of a first piston in a first bore connected to a second piston in a second bore.

FIG. 6 shows a schematic of a second piston in a second bore moving a first piston in a first bore through an extension of the first piston.

FIG. 7 shows an example of the tensioner of the first embodiment tensioning a chain through an arm.

DETAILED DESCRIPTION OF THE INVENTION

FIGS. 1-7 show tensioners using a passive control system to maintain tension of a chain span or belt. Passive control is defined as a system in which no feedback is used to regulate the position of a first piston relative to a second piston or between the position of a moveable sleeve relative to the position of a piston.

The tensioner systems of the present invention include a tensioner (described in further detail below) for a closed loop chain drive system used in an internal combustion engine. It may be utilized on a closed loop power transmission system between a driveshaft and at least one camshaft or on a balance shaft system between the driveshaft and a balance shaft. The tensioner system may also include an oil pump and be used with fuel pump drives. Additionally, the tensioner system of the present invention may also be used with belt drives.

FIG. 1 shows tensioner systems using passive control to maintain the position of a moveable sleeve 10 relative to a piston 3. Passive control is defined as a system in which no feedback is used to regulate the position of a movable sleeve 10 relative to a piston 3 of the tensioner 1. The passive system is in contrast to an active control system in which real time feedback of components of the engine are used to regulate the position of the movable sleeve 10.

The tensioner 1 includes a housing 2 having a first axially extending piston bore 2 a. Received within the bore 2 a of the housing 2 is a moveable sleeve 10. The moveable sleeve 10 has a first open end 13 a and a second open end 14 a which are separated by an inner flange 11 with a through hole 12. The first open end 13 a is defined by a top inner diameter portion 13, a top surface 15 of the inner flange 11 and the second open end 14 a is defined by a bottom inner diameter portion 14 and a bottom surface 16 of the inner flange 11. The through hole 12 of the inner flange 11 connects the first open end 13 a with the second open end 14 a. A top surface 17 of the moveable sleeve 10 is exposed to atmospheric pressure of the engine.

Received within the first open end 13 a of the moveable sleeve 10, defined by the top inner diameter portion 13 and the top surface 15 of the inner flange 11, is a hollow piston 3. Within the hollow piston 3 is a piston spring 4 biasing the piston 3 outwards from the housing 2. The piston spring 4 has a first end 4 a in contact with the inner portion 3 a of the hollow piston 3 and a second end 4 b in contact with a top surface 15 of the inner flange 11 of the moveable sleeve 10. It should be noted that while the piston 3 is shown as being hollow, the present invention could also apply to a solid piston, with the piston spring connecting the end of the piston.

Received within the second opening 14 a of the moveable sleeve 10, defined by the bottom inner diameter portion 14 and the bottom surface 16 of the inner flange 11, is a bias sleeve spring 5. The first end 5 a of the bias sleeve spring 5 is in contact with a bottom surface 16 of the inner flange 11 of the moveable sleeve 10 and the second end 5 b of the bias sleeve spring 5 is in contact with a check valve 8 of the bore 2 a. The bias sleeve spring 5 provides a bias force to maintain some outward force on the moveable sleeve 10. A pressure chamber 18 is formed between the top inner diameter portion 13 of the moveable sleeve 10, the bottom inner diameter portion 14 of the moveable sleeve 10, the bore 2 a of the housing, and the interior 3 a of the piston 3. The through hole 12 is present in the inner flange 11 and allows fluid to flow from the second opening 14 a to the first opening 13 a of the moveable sleeve 10.

At the bottom of the bore 2 a is an inlet supply line 6 which provides fluid to the pressure chamber 18 through an inlet check valve 8.

At least a portion of the moveable sleeve 10 is coupled to a second piston 20 received within a second axially extending piston bore 2 b of the housing 2 through a coupling 22. While the second piston 20 is shown as being connected to the top of the moveable sleeve 10, the connection can occur on other parts of the moveable sleeve 10. The coupling 22 may be a sleeve tab as shown in FIG. 1 or a flexible linkage. The second piston 20 does not need to be rigid or hard connection to the moveable sleeve 10 and can bias the moveable sleeve 10 from any contact point on the moveable sleeve 10.

Furthermore, while the second bore 2 b of the housing 2 is shown as being parallel to the first bore 2 a, the second bore 2 b may be perpendicular to the first bore 2 a or at some other angle relative to the first bore 2 a.

In an alternate embodiment, the orientation of the second piston 20 could be inverted or reoriented to act on a coupling 22 that then biases the moveable sleeve 10, outwards from the housing 2.

In yet another embodiment, the secondary piston 20 could also have a flange around its outer diameter with a chamber on either side as shown in International Application No. PCT/US2012/053830, which is hereby incorporated by reference.

At the bottom of the second bore 2 b is an inlet supply line 9 which provides fluid through an inlet check valve 7 to a pressure chamber 24 formed between the second piston 20 and the bore 2 b of the housing 2. The coupling 22 between the second piston 20 and the moveable sleeve 10 is such that, if the second piston 20 is moved, the moveable sleeve 10 moves and vice versa. The fluid from the inlet supply line 9 may also be controlled by a control valve (not shown).

When the tensioner 1 is tensioning a new chain, during operation, fluid is supplied to the first hydraulic chamber 18 from an inlet supply line 6 through an inlet check valve 8 to pressurize the first hydraulic chamber 18 and bias the piston 3 outward from the housing 2 in addition to the spring force from piston spring 4 biasing a span of the closed loop chain.

The supply providing fluid to the first bore 2 a through the first inlet supply line 6 may be the same as the supply providing fluid to second bore 2 b through inlet supply line 9. Alternatively, the supply supplying fluid to the first bore 2 a and the second bore 2 b of the housing 2 can be different.

When the tensioner 1 is tensioning a worn chain without high load, during operation, fluid is supplied to the first hydraulic chamber 18 through an inlet check valve 8 from an inlet supply line 6 to pressurize the first hydraulic chamber 18 and bias the piston 3 outward from the housing 2. The piston 3 is also biased outward from the housing 2 by the spring 4 to bias a span of the closed loop chain. As the chain wears, the piston 3 has to be biased further outwards from the housing 2 in order to adequately tension the chain. The bias sleeve spring 5 within the second open end 14 a of the moveable sleeve 10 biases the inner flange 11 outward from the housing 2, moving the end 4 b of the spring 4 further outwards from the housing 2 and towards the chain.

When the tensioner 1 is tensioning a worn chain during high dynamic chain load, the high dynamic load force from the chain (shown by the arrow) pushes the piston 3 inwards towards the housing 2 and then outwards from the housing 2, moving the second piston 20 inwards and outwards as well, pumping up the pressure or pressurizing the second pressure chamber 24, by drawing fluid through the inlet check valve 7 in the second bore 2 b of the housing 2. The pressurization of the second pressure chamber 24 in the second bore 2 a moves the second piston 20 and thus the moveable sleeve 10 outwards from the housing 2. The movement of the moveable sleeve 10 causes the inner flange 11 of the moveable sleeve 10 to exert an outward force on the piston 3 through the piston spring 4, opposing the inward force of the dynamic load.

Once the high load is removed from the piston 3, the second pressure chamber 24 is depressurized and fluid leaks out to the engine through clearance between the second bore 2 b and the second piston 20.

Within the tensioner system of the present invention, movement of the moveable sleeve 10 moves the second end 4 b of the piston spring 4 biasing the piston 3 outwards from the housing 2, and therefore the spring force acting on the piston 3 is variable allowing the piston 3 to continually tension the chain, even when the chain becomes worn and stretched.

Furthermore, a vent or pressure relief valve (not shown) may be present within the hollow piston 3.

Seals (not shown) may be present between the bore 2 a and the moveable sleeve 10 or any other place within the tensioner as necessary.

Hydraulic stiffness of the tensioner is created by the pressure chambers 18 and 24 of the tensioner and substantially prevents inward movement of the piston 3 and the moveable sleeve 10 towards the housing 2 when the chain span is under load.

In an alternate embodiment, the moveable sleeve 10 may be received within another sleeve in the first bore 2 a to aid in eliminating pressure that could result in undesired pump-up.

It should be noted that this is a mean position control device. It is unlikely that frequency response would be sufficient to dynamically vary the moveable sleeve position within an engine cycle. Pressure acting on the bottom surfaces of movable sleeve 10 may result in undesired pump-up. In an alternate embodiment, the moveable sleeve 10 may be received within another sleeve in the first bore 2 a to aid in eliminating pressure that could result in undesired pump-up. In another alternate embodiment, the piston 3 may fit over the outside of moveable sleeve 10 so the top and bottom surfaces of the moveable sleeve 10 are exposed to the same pressure.

FIGS. 2a-2b shows a tensioner of a second embodiment using passive control to tension a chain under various conditions; FIG. 2a is tensioning a chain without high loads; and FIG. 2b is tensioning a chain with high load.

The tensioner includes a housing 102 having a first axially extending bore 102 a parallel to a second axially extending bore 102 b. While the second bore 102 c of the housing 102 is shown as being parallel to the first bore 102 a, the second bore 102 c may be perpendicular to the first bore 102 a or at some other angle relative to the first bore 102 a.

Slidably received within the first axially extending bore 102 a is a first piston 103. The first piston 103 has a body with a first end 103 a, a second end 103 c, and a hollow interior 103 b. Present within the hollow interior 103 b of the first piston 103 is a first piston spring 104. The first piston spring 104 has a first end 104 a in contact with the interior 103 b of the first piston 103 or a volume reducer 105 and a second end 104 b in contact with a bottom 102 b of the first axially extending bore 102 a of the housing 102. A first pressure chamber 111 is formed between the first piston 103 and the first axially extending bore 102 a. Fluid is supplied to the first pressure chamber 111 through a first supply 106 through an inlet check valve 108. The first piston 103 is biased outwards from the housing 102 to bias a chain or belt through the first end 103 a of the first piston 103 by the force of the first piston spring 104 and the pressure of oil in the first pressure chamber 111.

Alternatively, the first piston 103 may not be hollow and the first piston spring 104 would contact the body of the first piston 103 and the bottom 102 b of the first axially extending bore 102 a.

The second axially extending bore 102 c receives a moveable sleeve 112. The moveable sleeve 112 has a first open end 112 a and a second open end 112 b which are separated by an inner flange 113. The first open end 112 a of the moveable sleeve 112 is defined by a top inner diameter portion 118 and a top surface 113 a of the inner flange 113. The second open end 112 b of the moveable sleeve 112 is defined by a bottom inner diameter portion 119 and a bottom surface 113 b of the inner flange 113. The top surface 112 d of the moveable sleeve 112 and top surface 113 a of the inner flange is exposed to atmospheric pressure of the engine.

Received within the first open end 112 a of the moveable sleeve 112 is a second piston 110 having a body with a first end 110 a and a second end 110 b. A second piston spring 115 biases the second piston 110 outwards from the first open end 112 a of the moveable sleeve 112 of the housing 102 so that the first end 110 a of the second piston 110 can apply a force to the chain 400, preferably through an arm 401 as shown in FIG. 7. The second piston spring 115 has a first end 115 a in contact with the second end 110 b of the second piston 110 and a second end 115 b in contact with the top surface 113 a of the inner flange 113.

Alternatively, the second piston 110 may be hollow and the first end 110 a of the second piston spring would contact a hollow interior of the second piston 110.

Received within the second open end 112 b of the moveable sleeve 112 is a bias sleeve spring 116 and an optional volume reducer 114. The first end 116 a of the bias sleeve spring 116 is in contact with a bottom surface 113 b of the inner flange 113 or the volume reducer 114 and a second end 116 b of the bias sleeve spring 116 is in contact with a bottom 102 d of the second axially extending bore 102 c of the housing 102. The bias sleeve spring 116 maintains the position of the moveable sleeve 112 within the second axially extending bore 102 c and prevents the moveable sleeve 112 from bottoming out within the second axially extending bore 102 c. The bias sleeve spring 116 preloads the second piston spring 115, in other words, moving the second end 115 b of the second piston spring 115 outwards from the housing 102. A second high pressure chamber 117 is formed between the bottom inner diameter portion 119 of the moveable sleeve 112, the bottom surface 113 b of the inner flange 113, and the bottom 102 d of the second axially extending bore 102 c. The volume reducer 114 may also be present within this chamber 117. There is no fluid communication between the first open end 112 a and the second open end 112 b of the moveable sleeve 112save for any leakage that may occur from the second high pressure chamber 117.

Fluid is supplied to the second high pressure chamber 117 through an inlet supply line 109 and preferably a check valve 107. The inlet supply 109 may or may not be connected to the inlet supply line 106.

The second piston spring 115 has a greater spring rate or spring constant than the first piston spring 104 or the bias sleeve spring 116.

Since there are two pistons 110, 103 to tension the chain span or belt, the leakage of the first pressure chamber 111 can be increased (as opposed to a conventional hydraulic tensioner where a certain mean pressure must be maintained within the pressure chamber to control the chain) to provide additional damping. The mean force required for chain control is supplied by the second piston 110 in the second axially extending bore 102 c.

When the tensioner is tensioning a new chain as shown in FIG. 2a , during operation, fluid is supplied to the first pressure chamber 111 from the first inlet supply 106 and through an inlet check valve 108 and biases the first piston 103 outwards from the housing 102 in addition to the spring force of the first piston spring 104, biasing a span of the closed loop chain 400 or belt as shown in FIG. 7. At the same time, the second piston 110 is also biased outwards from the moveable sleeve 112 by the second piston spring 115 to bias a span of the closed loop chain 400 or belt. Ideally, the first piston 103 and the second piston 110 are biased outwards from the housing 102 approximately the same amount. In other words, the first ends 103 a, 110 a of the first and second pistons 103, 110 are aligned as shown in FIGS. 2a and 7.

When the tensioner is tensioning a worn chain without high load, during operation, fluid is supplied to the first pressure chamber 111 through the first inlet supply 106 and through an inlet check valve 108 and biases the first piston 103 outwards from the housing 102 in addition to the spring force of the first piston spring 104, biasing a span of the closed loop chain 400 or belt. At the same time, the second piston 110 is also biased outwards from the moveable sleeve 112 by the second piston spring 115 due to the movement of the moveable sleeve 112 by the bias sleeve spring 116 to bias the span of the closed loop chain 400 or belt. As the chain wears, additional slack is present in the chain span and the first piston 103 and second piston 110 would need to be extended further outwards from the housing 102 to bias and adequately tension the chain 400.

When the tensioner is tensioning a chain during high dynamic chain load, the high dynamic load force from the chain (shown by the arrow) pushes the first piston 103 and the second piston 110 inwards towards the housing 102 and then outwards from the housing 102, pumping up the pressure or pressurizing the second pressure chamber 117, by drawing fluid through the inlet check valve 107 into the second bore 102 c of the housing 102. The pressurization of the second pressure chamber 117 in the second bore 102 c moves the moveable sleeve 112 outwards from the housing 102. The movement of the moveable sleeve 112 causes the inner flange 113 of the moveable sleeve 112 to exert an outward force on the second piston 110 through the second piston spring 115, opposing the inward force of the dynamic load.

Once the inward force of the dynamic load has been opposed, fluid within the second pressure chamber 117 leaks to the engine through the second axially extending bore 102 c or through the volume reducer 114. This leakage reduces the mean pressure present within the second pressure chamber 117.

It should be noted that at all operating conditions, the pressure in the second pressure chamber 117 will pump up to maintain a minimum preload in the second piston spring 115. When the force or preload in the second piston spring 115 gets too low, the moveable sleeve 112 moves out from the housing, due to the bias sleeve spring 116 and pressure in the second pressure chamber 117 and draws more oil in through the inlet check valve 107.

Therefore, the first piston 103 in the first axially extending bore 102 a provides the dominant damping of the chain span 400 or belt and the second piston 110 in the second axially extending bore 102 c provides the dominant and automatically adjusting spring force. The tensioner of the present invention automatically adjusts the mean tension force to keep the chain tension as low as possible without sacrificing chain control, significantly improving drive efficiency at new chain conditions and conditions with dynamic loads.

FIGS. 3a-3b shows a tensioner of a third embodiment using passive control to tension a chain under various conditions; FIG. 3a is tensioning a chain without high loads; and FIG. 3b is tensioning a chain with high load.

The tensioner includes a housing 102 having a first axially extending bore 102 a parallel to a second axially extending bore 102 c. While the second bore 102 c of the housing 102 is shown as being parallel to the first bore 102 a, the second bore 102 c may be perpendicular to the first bore 102 a or at some other angle relative to the first bore 102 a.

Slidably received within the first axially extending bore 102 a is a first piston 103. The first piston 103 has a body with a first end 103 a, a second end 103 c, and a hollow interior 103 b. Present within the hollow interior 103 b of the first piston 103 is a first piston spring 104. The first piston spring 104 has a first end 104 a in contact with the interior 103 b of the first piston 103 or a volume reducer 105 and a second end 104 b in contact with a bottom 102 b of the first axially extending bore 102 a of the housing 102. A first pressure chamber 111 is formed between the first piston 103 and the first axially extending bore 102 a. Fluid is supplied to the first pressure chamber through a first supply 106 through an inlet check valve 108. The first piston 103 is biased outwards from the housing 102 to bias the chain through the first end 103 a of the first piston by the force of the first piston spring 104 and the pressure of oil in the first pressure chamber 111.

Alternatively, the first piston 103 may not be hollow and the first piston spring 104 would contact the body of the first piston 103 and the bottom 102 b of the first axially extending bore 102 a.

The second axially extending bore 102 c slidably receives a second external piston 150 and a third piston 152. The second external piston 150 has a body with a first end 150 a, a second end 150 c, and a hollow interior 150 b. Present within the hollow interior 150 b is a second piston spring 151 for biasing the second piston 150 outwards from the housing 102. The second piston spring 151 has a first end 151 a in contact with the interior 150 b of the second external piston 150 and a second end 151 b in contact with a first end 152 a of the third piston 152. Alternatively, the second external piston 150 may not be hollow and the first end 151 a of the second piston spring 151 would contact the body of the second external piston 150.

The third piston 152 has a body with a first end 152 a, a second end 152 c, and a hollow interior 152 b. Present within the hollow interior 152 b is a third piston spring 154 for biasing the third piston 152 outwards from the housing and preloading the second piston spring 151, in other words moving the second end 151 b of the second piston spring 152 outwards from the housing 102. The third piston spring 154 has a first end 154 a in contact with the hollow interior 152 b or a volume reducer 153 and the second end 154 b is in contact with the bottom 102 c of the second axially extending bore 102 c of the housing 102.

A second high pressure chamber 155 is formed between the hollow interior 152 b, the second axially extending bore 102 c, and the third piston spring 154. Fluid is supplied to the second high pressure chamber 155 through an inlet supply 109 and preferably a check valve 107. The inlet supply 109 may or may not be connected to the inlet supply line 106.

There is no fluid communication between the hollow interior 150 b of the second piston 150 and the second high pressure chamber 155 save for any leakage that may occur.

The second piston spring 151 has a greater spring rate or spring constant than the first piston spring 104 and the third piston spring 154.

Since there are two pistons 150, 103 to tension the chain span or belt, the leakage of the first pressure chamber 111 can be increased (as opposed to a conventional hydraulic tensioner where a certain mean pressure must be maintained within the pressure chamber to control the chain) to provide additional damping. The mean force required for chain control is supplied by the second piston 150 in the second axially extending bore 102 c.

When the tensioner is tensioning a new chain as shown in FIG. 3a , during operation, fluid is supplied to the first pressure chamber 111 from the first inlet supply 106 and through an inlet check valve 108 and biases the first piston 103 outwards from the housing 102 in addition to the spring force of the first piston spring 104, biasing a span of the closed loop chain 400 or belt as shown in FIG. 7. At the same time, the second piston 150 is also biased outwards from the second axially extending bore 102 c by the second piston spring 151 to bias a span of the closed loop chain 400 or belt. Ideally, the first piston 103 and the second piston 150 are biased outwards from the housing 102 approximately the same amount. In other words, the first ends 103 a, 150 a of the first and the second pistons 103, 150 are aligned as shown in FIGS. 3a and 7.

When the tensioner is tensioning a worn chain without high load, during operation, fluid is supplied to the first pressure chamber 111 through the first inlet supply 106 and through an inlet check valve 108 and biases the first piston 103 outwards from the housing 102 in addition to the spring force of the first piston spring 104, biasing a span of the closed loop chain 400 or belt. At the same time, the second piston 150 is also biased outwards further through the second piston spring 151 due to the movement of the third piston 152 by the third piston spring 154 to bias the span of the closed loop chain 400 or belt. As the chain wears further, additional slack is present in the chain span and the first piston 103 and second piston 150 would need to be extended further outwards from the housing 102 to bias and adequately tension the chain 400.

When the tensioner is tensioning a chain during high dynamic chain load, the high dynamic load force from the chain (shown by the arrow) pushes the first piston 103 and the second piston 150 inwards towards the housing 102 and then outwards from the housing 102, pumping up the pressure or pressurizing the second pressure chamber 155, by drawing fluid through the inlet check valve 107 into the second bore 102 c of the housing 102. The pressurization of the second pressure chamber 155 in the second bore 102 c moves the third piston 152 outwards from the housing 102. The movement of the third piston 152 causes the first end 152 a of the third piston 152 to exert an outward force on the second piston 150 through the second piston spring 151, opposing the inward force of the dynamic load.

Once the inward force of the dynamic load has been opposed, fluid within the second pressure chamber 155 leaks to the engine through the second axially extending bore 102 c or through the volume reducer 153. This leakage reduces the mean pressure present within the second pressure chamber 155.

It should be noted that at all operating conditions, the pressure in the second pressure chamber 155 will pump up to maintain a minimum preload in the second piston spring 151. When the force or preload in the second piston spring 151 gets too low, the third piston 152 moves out from the housing, due to the third piston spring 154 and pressure in the second pressure chamber 155 and draws more oil in through the inlet check valve 107.

Therefore, the first piston 103 in the first axially extending bore 102 a provides the dominant damping of the chain span or belt and the second piston 150 in the second axially extending bore 102 c provides the dominant and automatically adjusting spring force. The tensioner of the present invention automatically adjusts the mean tension force to keep the chain tension as low as possible without sacrificing chain control, significantly improving drive efficiency at new chain conditions and conditions with dynamic loads.

FIGS. 4a-4b shows a tensioner of a fourth embodiment using passive control to tension a chain under various conditions; FIG. 4a is tensioning a chain without high loads; and FIG. 4b is tensioning a chain with high load.

The tensioner includes a housing 102 having a first axially extending bore 102 a parallel to a second axially extending bore 102 b. While the second bore 102 c of the housing 102 is shown as being parallel to the first bore 102 a, the second bore 102 c may be perpendicular to the first bore 102 a or at some other angle relative to the first bore 102 a.

Slidably received within the first axially extending bore 102 a is a first piston 103. The first piston 103 has a body with a first end 103 a, a second end 103 c, and a hollow interior 103 b. Present within the hollow interior 103 b of the first piston 103 is a first piston spring 104. The first piston spring 104 has a first end 104 a in contact with the interior 103 b of the first piston 103 or a volume reducer 105 and a second end 104 b in contact with a bottom 102 b of the first axially extending bore 102 a of the housing 102. A first pressure chamber 111 is formed between the first piston 103 and the first axially extending bore 102 a. Fluid is supplied to the first pressure chamber through a first supply 106 through an inlet check valve 108. The first piston 103 is biased outwards from the housing 102 to bias the chain through the first end 103 a of the first piston 103 by the force of the first piston spring 104 and the pressure of oil in the first pressure chamber 111.

Alternatively, the first piston 103 may not be hollow and the first piston spring 104 would contact the body of the first piston 103 and the bottom 102 b of the first axially extending bore 102 a.

The second axially extending bore 102 b slidably receives a second piston 200. The second piston 200 has a body with a first end 200 a, a second end 200 c and a hollow interior 200 b. The hollow interior 200 b receives a shaft 202 a of a “Y” shaped internal piston 202. The shaft 202 a of the Y-shaped internal piston 202 is connected to a body with a first end 202 d, a second end 202 b and a hollow interior 202 c. Between the second end 200 c of the second piston 200 and the first end 202 d of the body of the internal piston 202 d is a second piston spring 201. The second piston spring 201 has a first end 201 a in contact with the second end 200 c of the second piston 200 and a second end 201 b in contact with the first end 202 d of the internal piston 202. The second piston spring 201 biases the second piston 200 outwards from the housing 102.

Alternatively, the second piston spring may be present between the shaft 202 a of the Y-shaped internal piston 202 and the hollow interior 200 b of the second piston 200.

Within the hollow interior 202 c of the internal piston 202 is an internal piston spring 204. The internal piston spring 204 has a first end 204 a in contact a hollow interior 202 c of the internal piston 202 or a volume reducer 206 and a second end 204 b in contact with the bottom 102 d of the second axially extending bore 102 c. The internal piston spring 204 biases the internal piston 202 outwards from the housing 102, biasing the second piston 200 outwards from the housing by changing the preload on the second piston spring 201. In other words, moving the second end 201 b of the second piston spring 201 outwards from the housing 102.

A second high pressure chamber 205 is formed between the hollow interior 202 c of the internal piston 202 and the bottom 102 d of the second axially extending bore 102 c of the housing 102. Fluid is supplied to the second pressure chamber 205 through an inlet supply 109 and preferably a check valve 107. The inlet line 109 may or may not be connected to the inlet supply line 106.

The second piston spring 201 has a greater spring rate or spring constant than the first piston spring 104 and the internal piston spring 204.

Since there are two pistons 200, 103 to tension the chain span or belt, the leakage of the first pressure chamber 111 can be increased (as opposed to a conventional hydraulic tensioner where a certain mean pressure must be maintained within the pressure chamber to control the chain) to provide additional damping. The mean force required for chain control is supplied by the second piston 200 in the second axially extending bore 102 c.

When the tensioner is tensioning a new chain as shown in FIG. 4a , during operation, fluid is supplied to the first pressure chamber 111 from the first inlet supply 106 and through an inlet check valve 108 and biases the first piston 103 outwards from the housing 102 in addition to the spring force of the first piston spring 104, biasing a span of the closed loop chain 400 or belt as shown in FIG. 7. At the same time, the second piston 200 is also biased outwards from the second axially extending bore 102 c by the second piston spring 201 to bias a span of the closed loop chain or belt. Ideally, the first piston 103 and the second piston 200 are biased outwards from the housing 102 approximately the same amount. In other words, the first ends 103 a, 200 a of the first and the second pistons 103, 200 are aligned as shown in FIGS. 4a and 7.

When the tensioner is tensioning a worn chain without high load, during operation, fluid is supplied to the first pressure chamber 111 through the first inlet supply 106 and through an inlet check valve 108 and biases the first piston 103 outwards from the housing 102 in addition to the spring force of the first piston spring 104, biasing a span of the closed loop chain 400 or belt. At the same time, the second piston 200 is also biased outwards further through the second piston spring 201 due to the movement of the internal piston 202 by the internal piston spring 204 to bias the span of the closed loop chain 400 or belt. As the chain wears, additional slack is present in the chain span and the first piston 103 and second piston 200 would need to be extended further outwards from the housing 102 to bias and adequately tension the chain 400.

When the tensioner is tensioning a chain during high dynamic chain load, the high dynamic load force from the chain (shown by the arrow) pushes the first piston 103 and the second piston 200 inwards towards the housing 102 and then outwards from the housing 102, pumping up the pressure or pressurizing the second pressure chamber 205, by drawing fluid through the inlet check valve 107 in the second bore 102 c of the housing 102. The pressurization of the second pressure chamber 205 in the second bore 102 c moves the internal piston 202 outwards from the housing 102. The movement of the internal piston 202 causes the first end 202 d of the internal piston 202 to exert an outward force on the second piston 200 through the second piston spring 201, opposing the inward force of the dynamic load.

Once the inward force of the dynamic load has been opposed, fluid within the second pressure chamber 205 leaks to the engine through the second axially extending bore 102 c or through the volume reducer 206. This leakage reduces the mean pressure present within the second pressure chamber 205.

It should be noted that at all operating conditions, the pressure in the second pressure chamber 205 will pump up to maintain a minimum preload in the second piston spring 201. When the force or preload in the second piston spring 201 gets too low, the internal piston 202 moves out from the housing, due to the internal piston spring 204 and pressure in the second pressure chamber 205 and draws more oil in through the inlet check valve 107.

Therefore, the first piston 103 in the first axially extending bore 102 a provides the dominant damping of the chain span or belt and the second piston 200 in the second axially extending bore 102 c provides the dominant and automatically adjusting spring force. The tensioner of the present invention automatically adjusts the mean tension force to keep the chain tension as low as possible without sacrificing chain control, significantly improving drive efficiency at new chain conditions and conditions with dynamic loads.

FIGS. 5-6 show different options for simultaneously controlling the first piston and the second piston of the embodiments of the present invention. Referring to FIG. 5, the first piston 103 and the second piston 150 are directly attached through a linkage 310. Therefore, the movement of the first piston 103 and the second piston 150 are tied to each other. When the first piston 103 and the second piston 150 are coupled, the first piston spring 104 is optional. It should be noted that while the linkage was shown with the tensioner of the third embodiment, it can similarly be applied to the tensioners of FIGS. 2a-2b and 4a -4 b.

FIG. 6 shows an alternate configuration in which the first piston has an extension 312 with a top surface 312 a and a bottom surface 312 b. The bottom surface 312 b of the extension 312 is pushed on by the second piston 150 as the second piston 150 is biased outwards from the housing 102. It should be noted that while the linkage was shown with the tensioner of the third embodiment, it can similarly be applied to the tensioners of FIGS. 2a-2b and 4a-4b . In this embodiment, the first piston spring 104 is optional.

The volume reducers shown in any of the above embodiments may be replaced with a pressure relief valve or vent.

It should also be noted that the tensioner of FIGS. 2a-2b is shown in FIG. 7, however any of the tensioners present in the application would work with the chain span.

In any of the above embodiments, the external first pistons and second pistons may have grooves on an outer circumference that engage and ratchet with a pawl or ratchet clip as known in the art.

Accordingly, it is to be understood that the embodiments of the invention herein described are merely illustrative of the application of the principles of the invention. Reference herein to details of the illustrated embodiments is not intended to limit the scope of the claims, which themselves recite those features regarded as essential to the invention. 

What is claimed is:
 1. A tensioner for a passive tensioner system tensioning a chain having a chain span or a belt comprising: a housing have a first bore with a first fluid input and a second bore with a second fluid input; a hollow moveable sleeve slidably received by the first bore comprising a hollow body defining a first open end and a second open end separated by an inner flange having a top surface, a bottom surface and a through hole; a first piston coaxially arranged within the moveable sleeve and received by the first open end of the movable sleeve; a piston spring in contact with the first piston for biasing the first piston outwards from the moveable sleeve, having a first piston spring end contacting the first piston and a second piston spring end contacting the top surface of a flange of the moveable sleeve; a bias spring received within the first bore of the housing and the hollow interior of the moveable sleeve, for biasing the moveable sleeve outwards from the housing, with a first bias spring end in contact with the bottom surface of the inner flange of the moveable sleeve and a second bias spring end; a first pressure chamber defined between the hollow moveable sleeve, hollow interior of the first piston the bias spring and the first bore of the housing and in fluid communication with the first fluid input; a second piston slidably received by the second bore of the housing and coupled to the moveable sleeve through a coupling; a second pressure chamber defined between the second piston and the second bore, in fluid communication with the second fluid input; a check valve between the second pressure chamber and the second fluid input; wherein when dynamic load from the chain or belt moves the first piston inwards and outwards from the housing, the second piston, coupled to the first piston, moves inwards into the housing and outwards into the housing, drawing fluid from the second fluid input and the check valve, into the second pressure chamber, creating a fluid pressure in the second pressure chamber, causing the movable sleeve to move outwards from the housing and exert an outward force on the first piston through the piston spring, opposing an inward force of the dynamic load.
 2. The tensioner of claim 1, wherein the first fluid input and the second fluid input are connected to the same fluid supply.
 3. The tensioner of claim 1, wherein the first fluid input and the second fluid input are connected to different fluid supplies.
 4. The tensioner of claim 1, wherein the first bore is parallel to the second bore.
 5. The tensioner of claim 1, wherein the coupling is flexible.
 6. The tensioner of claim 1, wherein the coupling is rigid.
 7. The tensioner of claim 1, wherein the piston further comprises a body having an open end and a closed end and a hollow interior having an inner diameter.
 8. The tensioner of claim 7, wherein the first piston spring end contacts the inner surface of the closed end of piston.
 9. The tensioner of claim 1, further comprising a check valve between the first fluid input and the first pressure chamber. 